US9631675B2 - Connection device for a shaft - Google Patents

Connection device for a shaft Download PDF

Info

Publication number
US9631675B2
US9631675B2 US14/851,582 US201514851582A US9631675B2 US 9631675 B2 US9631675 B2 US 9631675B2 US 201514851582 A US201514851582 A US 201514851582A US 9631675 B2 US9631675 B2 US 9631675B2
Authority
US
United States
Prior art keywords
end section
pipe segment
outer diameter
supporting ring
shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
US14/851,582
Other versions
US20160003304A1 (en
Inventor
Wolfgang Streinz
Armin Zeilner
Johann Reindl
Josef Hofstetter
Heinrich Gruenwald
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bayerische Motoren Werke AG
Original Assignee
Bayerische Motoren Werke AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Bayerische Motoren Werke AG filed Critical Bayerische Motoren Werke AG
Assigned to BAYERISCHE MOTOREN WERKE AKTIENGESELLSCHAFT reassignment BAYERISCHE MOTOREN WERKE AKTIENGESELLSCHAFT ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HOFSTETTER, JOSEF, GRUENWALD, HEINRICH, REINDL, JOHANN, STREINZ, WOLFGANG, ZEILNER, Armin
Publication of US20160003304A1 publication Critical patent/US20160003304A1/en
Application granted granted Critical
Publication of US9631675B2 publication Critical patent/US9631675B2/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/02—Shafts; Axles
    • F16C3/023—Shafts; Axles made of several parts, e.g. by welding
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C3/00—Shafts; Axles; Cranks; Eccentrics
    • F16C3/02—Shafts; Axles
    • F16C3/026—Shafts made of fibre reinforced resin
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/08—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key
    • F16D1/0852—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping between the mating surfaces of the hub and shaft
    • F16D1/0858—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping between the mating surfaces of the hub and shaft due to the elasticity of the hub (including shrink fits)
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/08—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key
    • F16D1/0852—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping between the mating surfaces of the hub and shaft
    • F16D1/087—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end with clamping hub; with hub and longitudinal key with radial clamping between the mating surfaces of the hub and shaft due to other loading elements in the hub or shaft
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/22—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or type of main drive shafting, e.g. cardan shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/06—Drive shafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
    • F16D2001/103—Quick-acting couplings in which the parts are connected by simply bringing them together axially the torque is transmitted via splined connections

Definitions

  • the invention relates to a connection device for a shaft, formed from an end section of a pipe segment.
  • Fiber-reinforced plastic materials play an increasingly important role in this respect. These have been used not only for motor vehicle body components but, for example, also for shafts (drive shafts). For this purpose, it is necessary to connect shafts made of fiber-reinforced plastics, particularly of CFRPs, with steel or aluminum components. In the case of a connection device of a drive shaft, high torsional moments are to be transmitted, so that correspondingly larger dimensions are selected, which are relatively heavy.
  • connection is constructed as knurled connections, where steel or aluminum attachment parts having a large wall thickness are pressed and glued into a CFRP pipe.
  • the steel or aluminum attachment parts are pipe-shaped and, in the state of the art, have a thickness of at least 4 mm. This ensures that the pipe segments will not radially collapse during the pressing-in. This is necessary in order to transmit the high torsional moments between the attachment part and the shaft without failure of the connection.
  • This connection frequently also determines the crash behavior, in which case the attachment part is pressed into the pipe. As a result of the many influencing variables, the crash forces may vary widely, causing the pipe to burst.
  • connection device For reducing the weight of the connection device, developers have always had the desire to construct the pipe-shaped attachment parts of steel or aluminum in a thin-walled fashion, in order to reduce the overall weight. However, a thin-walled design could not reliably transmit torsional moments and does not supply sufficient stability in the event of a crash.
  • connection device for a shaft to an attachment part that is capable of transmitting the torsional moments required in motor vehicle construction with the customary reliability, and simultaneously meeting necessary crash requirements with respect to essential energy absorption.
  • connection device for a shaft formed of an end section of a pipe segment, over which the shaft can be pushed.
  • an external toothing is provided on a radial outer surface of an end section of the pipe segment.
  • a supporting ring is arranged in the interior of the end section of the pipe segment.
  • the use of a supporting ring is advantageous in that the end section of the pipe segment is stabilized precisely in the area where the shaft is also arranged.
  • the supporting ring is pressed into the end section of the pipe segment, in order for the end section to withstand the high radial forces when the shaft is pressed onto the end section.
  • the end section of the pipe segment therefore retains its original shape, although its wall thickness is considerably reduced compared to the end sections used in prior art.
  • the supporting ring is preferably constructed of steel.
  • the advantageous use of the supporting ring has the result that a measurement of 1.2 to 2.5 mm may be selected for the end section.
  • a wall thickness of 1.5 to 2.2 mm, and even more preferably, a wall thickness of 1.6 to 1.9 mm can be selected.
  • the outside diameter of the supporting ring is minimally larger than the inside diameter of the end section of the pipe segment, so that, after the pressing into the end section, the supporting ring is fixed in the end section as a press fit.
  • the supporting ring is preferably arranged in the axial direction in the center in the area of the end section in which the external toothing is provided.
  • the supporting ring has an axial dimension of from 10 to 20 mm, preferably an axial dimension of from 10 to 15 mm. It is thereby ensured that sufficient support is provided with respect to the radial forces arising during the pressing-on of the shaft, without any canceling of the weight advantage as a result of the thin-walled construction of the end section of the pipe segment.
  • the weight savings of a pipe section of, for example, a wall thickness of 1.8 mm compared to those of the prior art having a wall thickness of 4 mm amount to at least 40%.
  • An implementation of the external toothing of the end section of the pipe segment as a knurling is preferred and is generated by milled knurling.
  • a radial outer surface created by milled knurling presents a large contact surface for the shaft to be pushed on later, so that high torsional moments can be transmitted, which in each case reach a magnitude desired for vehicle construction.
  • connection device is characterized in that standard pipes are used whose end section is reduced to a predefined diameter.
  • a predefined pipe for example, of a diameter of 70 mm, can be reduced to an end diameter of 60 or 55 mm, depending on which inside shaft diameter is to be pushed on.
  • Special-grade cardan tubes for example, are used as pipe segments.
  • a bead is provided at the end section, which bead forms a predetermined breaking point.
  • Such predetermined breaking points are provided for meeting crash demands, in which case the component fails in a predetermined direction in the event of a predefined load.
  • the bead is formed by a circumferential radial bulging adjoining the knurling or external toothing.
  • a balancing range of the pipe segment is provided in the axial direction adjacent to the end section, in which balancing range balancing weights can be mounted.
  • the connection device is used for drive shafts, the balancing of the drive shaft can take place directly at the area of the connection or adapter.
  • Balancing weights are, for example, welded on or are fixed in a different manner known from the state of the art.
  • FIG. 1 is a lateral, partially sectional view of the connection device according to an embodiment of the invention.
  • FIG. 1 is a lateral view of the connection device, the lower half being illustrated as a sectional view.
  • the shaft 2 is pressed onto the end section 3 of the pipe segment 4 , so that the illustrated implementation shows the connection device 1 in its end (connected) condition.
  • the radial outer surface of the end section 3 of the pipe segment 4 has a knurling 6 , which extends in the axial direction essentially from the axial end edge of the shaft 2 to the section indicated by reference number 6 ′.
  • the indicated implementation is schematic, but the preferred wall thickness of the end section 3 , measured at the thickest point marked by reference number 3 , is not larger than 2.5 mm, in the illustrated implementation, 1.8 mm.
  • a supporting ring 5 is pressed in to an axial center area of the knurling 6 .
  • the wall thickness of the supporting ring 5 corresponds essentially to the wall thickness of the end section.
  • the outside diameter of the supporting ring 5 is minimally larger than the inside diameter of the end section 3 .
  • the supporting ring 5 extends over a predefined length, in the concrete example, over 15 mm.
  • the pipe segment 4 of the connection device 1 has a bead 7 .
  • the bead 7 is provided by radially outward-pressed material of the pipe segment 4 .
  • the balancing area 8 of the pipe segment 4 is provided adjoining the end section 3 or the bead 7 in the axial direction, in which balancing weights (not shown) are connected by welding.
  • the pipe segment 4 is made of steel and the shaft is made of CFRP.
  • an adhesive and sealing bead may additionally be provided between the shaft 2 and the end section 3 of the pipe segment 4 .
  • This sealing bead would preferably be arranged in the circumferential direction in the area marked by reference number 6 .
  • the invention is not limited to the above-described embodiment.
  • a number of variants are contemplated, which use the illustrated solution also in the case of basically different implementations. It may, for example, be provided to construct the supporting ring to be thicker, but thinner in the axial direction. It is also contemplated to use an end section 3 of the pipe segment 4 with a diameter smaller than that marked D, in that the end section is further reduced and can therefore be adapted to shafts 2 of a smaller construction.

Abstract

A lightweight construction connection device is provided for a shaft, formed from an end section of a pipe segment, over which the shaft can be slid and having a knurling on the radial outside surface thereof. A support ring is arranged in the interior of the end section of the pipe segment.

Description

CROSS REFERENCE TO RELATED APPLICATIONS
This application is a continuation of PCT International Application No. PCT/EP2014/053522, filed Feb. 24, 2014, which claims priority under 35 U.S.C. §119 from German Patent Application No. 10 2013 204 181.0, filed Mar. 12, 2013, the entire disclosures of which are herein expressly incorporated by reference.
BACKGROUND AND SUMMARY OF THE INVENTION
The invention relates to a connection device for a shaft, formed from an end section of a pipe segment.
For the development of new parts, the topic of a lightweight construction is particularly significant in various technical fields, especially in the field of automotive engineering. Fiber-reinforced plastic materials play an increasingly important role in this respect. These have been used not only for motor vehicle body components but, for example, also for shafts (drive shafts). For this purpose, it is necessary to connect shafts made of fiber-reinforced plastics, particularly of CFRPs, with steel or aluminum components. In the case of a connection device of a drive shaft, high torsional moments are to be transmitted, so that correspondingly larger dimensions are selected, which are relatively heavy.
From the state of the art, it is known to ensure that such connections are constructed as knurled connections, where steel or aluminum attachment parts having a large wall thickness are pressed and glued into a CFRP pipe. The steel or aluminum attachment parts are pipe-shaped and, in the state of the art, have a thickness of at least 4 mm. This ensures that the pipe segments will not radially collapse during the pressing-in. This is necessary in order to transmit the high torsional moments between the attachment part and the shaft without failure of the connection. This connection frequently also determines the crash behavior, in which case the attachment part is pressed into the pipe. As a result of the many influencing variables, the crash forces may vary widely, causing the pipe to burst.
However, the use of thick-walled pipes having a wall thickness of 4 mm or more will result in considerable overall weight of the connection of the shaft and the steel or aluminum attachment part, whereby the significant weight advantage is impaired by the use of a shaft made of the CFRP material.
For reducing the weight of the connection device, developers have always had the desire to construct the pipe-shaped attachment parts of steel or aluminum in a thin-walled fashion, in order to reduce the overall weight. However, a thin-walled design could not reliably transmit torsional moments and does not supply sufficient stability in the event of a crash.
It is therefore an object of the present invention to provide a connection device for a shaft to an attachment part that is capable of transmitting the torsional moments required in motor vehicle construction with the customary reliability, and simultaneously meeting necessary crash requirements with respect to essential energy absorption.
This and other objects are achieved by a connection device for a shaft formed of an end section of a pipe segment, over which the shaft can be pushed. On a radial outer surface of an end section of the pipe segment, an external toothing is provided. A supporting ring is arranged in the interior of the end section of the pipe segment.
The use of a supporting ring is advantageous in that the end section of the pipe segment is stabilized precisely in the area where the shaft is also arranged. In a preferred embodiment, the supporting ring is pressed into the end section of the pipe segment, in order for the end section to withstand the high radial forces when the shaft is pressed onto the end section. The end section of the pipe segment therefore retains its original shape, although its wall thickness is considerably reduced compared to the end sections used in prior art. The supporting ring is preferably constructed of steel.
The advantageous use of the supporting ring has the result that a measurement of 1.2 to 2.5 mm may be selected for the end section. Preferably, a wall thickness of 1.5 to 2.2 mm, and even more preferably, a wall thickness of 1.6 to 1.9 mm can be selected. The outside diameter of the supporting ring is minimally larger than the inside diameter of the end section of the pipe segment, so that, after the pressing into the end section, the supporting ring is fixed in the end section as a press fit. The supporting ring is preferably arranged in the axial direction in the center in the area of the end section in which the external toothing is provided.
In a preferred embodiment, the supporting ring has an axial dimension of from 10 to 20 mm, preferably an axial dimension of from 10 to 15 mm. It is thereby ensured that sufficient support is provided with respect to the radial forces arising during the pressing-on of the shaft, without any canceling of the weight advantage as a result of the thin-walled construction of the end section of the pipe segment. The weight savings of a pipe section of, for example, a wall thickness of 1.8 mm compared to those of the prior art having a wall thickness of 4 mm amount to at least 40%.
An implementation of the external toothing of the end section of the pipe segment as a knurling is preferred and is generated by milled knurling. A radial outer surface created by milled knurling presents a large contact surface for the shaft to be pushed on later, so that high torsional moments can be transmitted, which in each case reach a magnitude desired for vehicle construction.
Furthermore, the connection device is characterized in that standard pipes are used whose end section is reduced to a predefined diameter. This has the advantage that a predefined pipe, for example, of a diameter of 70 mm, can be reduced to an end diameter of 60 or 55 mm, depending on which inside shaft diameter is to be pushed on. As a result, it becomes possible to weld together identical parts of the drive shaft assembly or to meet packaging demands customary in vehicle construction. Special-grade cardan tubes, for example, are used as pipe segments.
In a preferred embodiment, a bead is provided at the end section, which bead forms a predetermined breaking point. Such predetermined breaking points are provided for meeting crash demands, in which case the component fails in a predetermined direction in the event of a predefined load. The bead is formed by a circumferential radial bulging adjoining the knurling or external toothing.
In a preferred embodiment of the invention, it is further provided that a balancing range of the pipe segment is provided in the axial direction adjacent to the end section, in which balancing range balancing weights can be mounted. Thus, when the connection device is used for drive shafts, the balancing of the drive shaft can take place directly at the area of the connection or adapter. Balancing weights are, for example, welded on or are fixed in a different manner known from the state of the art.
Other advantageous further developments of the invention are characterized in the subclaims and are illustrated in detail in the following together with the description of the preferred embodiment of the invention by means of the figures.
BRIEF DESCRIPTION OF THE DRAWING
FIG. 1 is a lateral, partially sectional view of the connection device according to an embodiment of the invention.
 DETAILED DESCRIPTION OF THE DRAWING
FIG. 1 is a lateral view of the connection device, the lower half being illustrated as a sectional view. The shaft 2 is pressed onto the end section 3 of the pipe segment 4, so that the illustrated implementation shows the connection device 1 in its end (connected) condition. The radial outer surface of the end section 3 of the pipe segment 4 has a knurling 6, which extends in the axial direction essentially from the axial end edge of the shaft 2 to the section indicated by reference number 6′. As an example, the indicated implementation is schematic, but the preferred wall thickness of the end section 3, measured at the thickest point marked by reference number 3, is not larger than 2.5 mm, in the illustrated implementation, 1.8 mm.
In the end section 3 of the pipe segment, a supporting ring 5 is pressed in to an axial center area of the knurling 6. The wall thickness of the supporting ring 5 corresponds essentially to the wall thickness of the end section. For ensuring a press fit, the outside diameter of the supporting ring 5 is minimally larger than the inside diameter of the end section 3. In the axial direction, the supporting ring 5 extends over a predefined length, in the concrete example, over 15 mm.
In an area, which adjoins the knurled section of the end section 3 in the axial direction, the pipe segment 4 of the connection device 1 has a bead 7. The bead 7 is provided by radially outward-pressed material of the pipe segment 4. The balancing area 8 of the pipe segment 4 is provided adjoining the end section 3 or the bead 7 in the axial direction, in which balancing weights (not shown) are connected by welding. In the illustrated embodiment, the pipe segment 4 is made of steel and the shaft is made of CFRP.
For the purpose of sealing off dirt and moisture from the outside, an adhesive and sealing bead (not shown) may additionally be provided between the shaft 2 and the end section 3 of the pipe segment 4. This sealing bead would preferably be arranged in the circumferential direction in the area marked by reference number 6.
In its implementation, the invention is not limited to the above-described embodiment. On the contrary, a number of variants are contemplated, which use the illustrated solution also in the case of basically different implementations. It may, for example, be provided to construct the supporting ring to be thicker, but thinner in the axial direction. It is also contemplated to use an end section 3 of the pipe segment 4 with a diameter smaller than that marked D, in that the end section is further reduced and can therefore be adapted to shafts 2 of a smaller construction.
The foregoing disclosure has been set forth merely to illustrate the invention and is not intended to be limiting. Since modifications of the disclosed embodiments incorporating the spirit and substance of the invention may occur to persons skilled in the art, the invention should be construed to include everything within the scope of the appended claims and equivalents thereof.

Claims (18)

What is claimed is:
1. A connection for a shaft, comprising:
a pipe segment having an end section, the end section being located at a longitudinal end of the pipe segment, a radial outer surface of the end section of the pipe segment having external toothing;
a radially protruding bead that is adjacent to the end section, and having an outer diameter that is larger than an outer diameter of the end section;
a balancing area that is located on an opposite side of the radially protruding bead from the end section; and
a supporting ring arranged in an interior of the end section of the pipe segment, wherein
the end section of the pipe segment having the supporting ring and the radial outer surface with the external tooting are configured for the shaft to be slid over the end section,
an outer diameter of the end section of the pipe segment gradually decreases to a predetermined diameter along a longitudinal direction of the pipe segment, and
the balancing area having an outer diameter that is smaller than the outer diameter of the end section.
2. The connection according to claim 1, wherein the end section of the pipe segment has a thin-walled construction with a wall thickness of between 1.2 and 2.5 millimeters.
3. The connection according to claim 2, wherein an outer diameter of the supporting ring is larger than an inner diameter of the end section of the pipe segment.
4. The connection according to claim 3, further comprising a press-fit connection of the supporting ring in the interior of the end section of the pipe segment.
5. The connection according to claim 4, wherein the supporting ring has an axial dimension of from 10 to 20 millimeters.
6. The connection according to claim 1, wherein an outer diameter of the supporting ring is larger than an inner diameter of the end section of the pipe segment.
7. The connection according to claim 1, further comprising a press-fit connection of the supporting ring in the interior of the end section of the pipe segment.
8. The connection according to claim 1, wherein the supporting ring has an axial dimension of from 10 to 20 millimeters.
9. The connection according to claim 1, wherein the external toothing is a milled knurling.
10. The connection according to claim 9, wherein the milled knurling extends in a longitudinal axis of the end section of the pipe segment.
11. The connection according to claim 1, wherein the balancing area is configured to allow balancing weights to be mounted.
12. The connection according to claim 1, wherein the pipe segment is made of steel.
13. The connection according to claim 1, wherein
the support ring is disposed in the middle of the end section, and
the supporting ring extends, along a longitudinal direction of the end section, about one third of a length of the end section.
14. A connection for a shaft, comprising:
a pipe segment having
on an outer surface thereof a radially protruding bead, and external teeth disposed on a radial outer surface of the pipe segment adjacent to the radially protruding bead;
a balancing area that is located on an opposite side of the radially protruding bead from an end section; and
a supporting ring arranged in an interior of the end section of the pipe segment, wherein
the end section of the pipe segment having the supporting ring and the radial outer surface with the external teeth is configured for the shaft to be slid over the end section,
the support ring is disposed in the middle of the end section,
the supporting ring extends, along a longitudinal direction of the end section, about one third of a length of the end section,
the radially protruding bead defines a breaking location at which the connection breaks when a predefined load is applied to the connection,
the end section is located at a longitudinal end of the pipe segment,
the radially protruding bead has an outer diameter that is larger than an outer diameter of the end section, and
the balancing area has an outer diameter that is smaller than the outer diameter of the end section.
15. A connector assembly comprising:
a shaft;
a pipe segment having
a radially protruding bead, and external teeth disposed on a radial outer surface of the pipe segment adjacent to the radially protruding bead; and
a supporting ring arranged in an interior of an end section of the pipe segment; and
a balancing area that is located on an opposite side of the radially protruding bead from the end section, wherein
the end section of the pipe segment having the supporting ring and the radial outer surface with the external teeth are configured for the shaft to be slid over the end section,
an outer diameter of the end section of the pipe segment gradually decreases to a predetermined diameter along a longitudinal direction of the pipe segment, to thereby accept cooperation with shafts of different sizes,
the radially protruding bead defines a breaking location at which the connector assembly breaks when a predefined load is applied to the connector assembly,
the end section is located at a longitudinal end of the pipe segment,
the radially protruding bead has an outer diameter that is larger than an outer diameter of the end section, and
the balancing area has an outer diameter that is smaller than the outer diameter of the end section.
16. The connector assembly according to claim 15, wherein the shaft is made of fiber-reinforced plastic.
17. The connector assembly according to claim 16, wherein the fiber-reinforced plastic is a carbon fiber reinforced plastic.
18. The connector assembly according to claim 17, wherein the shaft is a drive shaft of a motor vehicle.
US14/851,582 2013-03-12 2015-09-11 Connection device for a shaft Active US9631675B2 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102013204181 2013-03-12
DE102013204181.0A DE102013204181A1 (en) 2013-03-12 2013-03-12 Connecting device for a shaft
DE102013204181.0 2013-03-12
PCT/EP2014/053522 WO2014139785A1 (en) 2013-03-12 2014-02-24 Connection device for a shaft

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2014/053522 Continuation WO2014139785A1 (en) 2013-03-12 2014-02-24 Connection device for a shaft

Publications (2)

Publication Number Publication Date
US20160003304A1 US20160003304A1 (en) 2016-01-07
US9631675B2 true US9631675B2 (en) 2017-04-25

Family

ID=50151299

Family Applications (1)

Application Number Title Priority Date Filing Date
US14/851,582 Active US9631675B2 (en) 2013-03-12 2015-09-11 Connection device for a shaft

Country Status (5)

Country Link
US (1) US9631675B2 (en)
EP (1) EP2971813B1 (en)
CN (1) CN104919194B (en)
DE (1) DE102013204181A1 (en)
WO (1) WO2014139785A1 (en)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015209110B4 (en) 2015-05-19 2022-08-18 Bayerische Motoren Werke Aktiengesellschaft Connection device for a drive train
SE541072C2 (en) * 2015-11-23 2019-03-26 Scania Cv Ab Driveshaft assembly and method for its production
CN105840674A (en) * 2016-04-29 2016-08-10 苏州鼎隆精密机械制造有限公司 Screw barrel connection structure
CN105840629A (en) * 2016-04-29 2016-08-10 苏州鼎隆精密机械制造有限公司 Countersunk head and thread sleeve connecting structure
CN105840673A (en) * 2016-04-29 2016-08-10 苏州鼎隆精密机械制造有限公司 Tight connection structure for countersunk head thread sleeve
CN105840638A (en) * 2016-04-29 2016-08-10 苏州鼎隆精密机械制造有限公司 Tight connecting structure for thread sleeve
DE102019210419A1 (en) * 2019-07-15 2021-01-21 Rolls-Royce Deutschland Ltd & Co Kg Shaft connection

Citations (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB698902A (en) 1950-03-11 1953-10-28 Daimler Benz Ag Improvements relating to propeller shafts for motor vehicles
US4173128A (en) 1978-05-23 1979-11-06 Grumman Aerospace Corporation Composite drive shaft
US4238539A (en) * 1979-05-29 1980-12-09 Celanese Corporation Fiber reinforced composite shaft with metallic connector sleeves mounted by a knurl interlock
US4265951A (en) * 1978-03-27 1981-05-05 Celanese Corporation Fiber reinforced composite shaft with metallic connector sleeves mounted by longitudinal groove interlock
GB2071812A (en) 1980-03-01 1981-09-23 Daimler Benz Ag Connecting junction for fibre reinforced plastics tube
FR2564538A1 (en) * 1984-05-18 1985-11-22 Skf Cie Ste Financiere Immobil Rotary transmission shaft.
DE3926427C1 (en) * 1989-08-10 1990-12-20 Audi Ag, 8070 Ingolstadt, De
FR2653505A1 (en) * 1989-10-20 1991-04-26 Framatome Sa Coupling device for rotating shafts
US5253947A (en) * 1990-10-23 1993-10-19 Gkn Automotive Ag Connection between a tubular shaft made of a fiber composite material and a metal journal, as well as a method of producing such a connection
US5601493A (en) 1992-10-22 1997-02-11 Sumitomo Chemical Company Limited Drive shaft made of fiber reinforced plastics, and method for connecting pipe made of fire-reinforced plastics
DE19842821A1 (en) 1998-09-18 2000-04-20 Volkswagen Ag Carbon fibre two-part automotive drive shaft union has interlocking fibres transmitting high torque value
DE10150616C1 (en) * 2001-10-12 2003-02-06 Daimler Chrysler Ag Connection between an inner jacket of steering column of a motor vehicle and sleeve-like holder comprises on the jacket two radially protruding stops and a form-locking element interacting with counter form-locking element on holder
DE10208706A1 (en) 2002-02-25 2003-09-11 Takata Petri Ag Vehicle steering wheel frame, has spokes joined to hub via common deformation part
US20040082394A1 (en) 2002-10-23 2004-04-29 Lee Dai Gil Hybrid propeller shaft made of metal and composite material and method of manufacturing the same
DE10312056B3 (en) 2003-03-18 2004-11-18 Spicer Gelenkwellenbau Gmbh & Co. Kg Balancing agent for a cardan shaft
WO2007036343A1 (en) 2005-09-27 2007-04-05 Shaft-Form-Engineering Gmbh Joint shaft and roller displacement unit therefor
DE102007001253A1 (en) 2006-01-17 2007-11-22 Crompton Technology Group Ltd., Banbury Configuration of a connection for a transmission shaft
CN101272927A (en) 2005-09-27 2008-09-24 轴造型工程公司 Joint shaft and roller displacement unit therefor
CN101292093A (en) 2005-10-17 2008-10-22 博格华纳公司 Coupling device for transmitting a torque
CN102472310A (en) 2009-08-31 2012-05-23 藤仓橡胶工业株式会社 Frp-made drive shaft

Patent Citations (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB698902A (en) 1950-03-11 1953-10-28 Daimler Benz Ag Improvements relating to propeller shafts for motor vehicles
US4265951A (en) * 1978-03-27 1981-05-05 Celanese Corporation Fiber reinforced composite shaft with metallic connector sleeves mounted by longitudinal groove interlock
US4173128A (en) 1978-05-23 1979-11-06 Grumman Aerospace Corporation Composite drive shaft
US4238539A (en) * 1979-05-29 1980-12-09 Celanese Corporation Fiber reinforced composite shaft with metallic connector sleeves mounted by a knurl interlock
GB2071812A (en) 1980-03-01 1981-09-23 Daimler Benz Ag Connecting junction for fibre reinforced plastics tube
FR2564538A1 (en) * 1984-05-18 1985-11-22 Skf Cie Ste Financiere Immobil Rotary transmission shaft.
DE3926427C1 (en) * 1989-08-10 1990-12-20 Audi Ag, 8070 Ingolstadt, De
FR2653505A1 (en) * 1989-10-20 1991-04-26 Framatome Sa Coupling device for rotating shafts
US5253947A (en) * 1990-10-23 1993-10-19 Gkn Automotive Ag Connection between a tubular shaft made of a fiber composite material and a metal journal, as well as a method of producing such a connection
US5601493A (en) 1992-10-22 1997-02-11 Sumitomo Chemical Company Limited Drive shaft made of fiber reinforced plastics, and method for connecting pipe made of fire-reinforced plastics
DE19842821A1 (en) 1998-09-18 2000-04-20 Volkswagen Ag Carbon fibre two-part automotive drive shaft union has interlocking fibres transmitting high torque value
DE10150616C1 (en) * 2001-10-12 2003-02-06 Daimler Chrysler Ag Connection between an inner jacket of steering column of a motor vehicle and sleeve-like holder comprises on the jacket two radially protruding stops and a form-locking element interacting with counter form-locking element on holder
DE10208706A1 (en) 2002-02-25 2003-09-11 Takata Petri Ag Vehicle steering wheel frame, has spokes joined to hub via common deformation part
US20040082394A1 (en) 2002-10-23 2004-04-29 Lee Dai Gil Hybrid propeller shaft made of metal and composite material and method of manufacturing the same
DE10312056B3 (en) 2003-03-18 2004-11-18 Spicer Gelenkwellenbau Gmbh & Co. Kg Balancing agent for a cardan shaft
WO2007036343A1 (en) 2005-09-27 2007-04-05 Shaft-Form-Engineering Gmbh Joint shaft and roller displacement unit therefor
CN101272927A (en) 2005-09-27 2008-09-24 轴造型工程公司 Joint shaft and roller displacement unit therefor
US20080248886A1 (en) 2005-09-27 2008-10-09 Shaft-Form Emgineering Gmbh Joint Shaft and Roller Displacement
CN101292093A (en) 2005-10-17 2008-10-22 博格华纳公司 Coupling device for transmitting a torque
US20090203453A1 (en) 2005-10-17 2009-08-13 Johannes Heinrich Coupling Device for Transmitting a Torque
DE102007001253A1 (en) 2006-01-17 2007-11-22 Crompton Technology Group Ltd., Banbury Configuration of a connection for a transmission shaft
US20080012329A1 (en) 2006-01-17 2008-01-17 Crompton Technology Group Limited Transmission shaft joint design
CN102472310A (en) 2009-08-31 2012-05-23 藤仓橡胶工业株式会社 Frp-made drive shaft
US20120157217A1 (en) 2009-08-31 2012-06-21 Fujikura Rubber Ltd. Frp drive shaft

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
Chinese Office Action issued in counterpart Chinese Application No. 201480004702.5 dated Sep. 5, 2016 with English translation (14 pages).
European Office Action issued in counterpart European Application No. 14 705 794.7 dated Oct. 20, 2016 (five (5) pages).

Also Published As

Publication number Publication date
US20160003304A1 (en) 2016-01-07
EP2971813A1 (en) 2016-01-20
WO2014139785A1 (en) 2014-09-18
CN104919194A (en) 2015-09-16
CN104919194B (en) 2018-03-27
DE102013204181A1 (en) 2014-09-18
EP2971813B1 (en) 2017-07-12

Similar Documents

Publication Publication Date Title
US9631675B2 (en) Connection device for a shaft
US20130156498A1 (en) Bracket-less clamping assembly
US9511664B2 (en) Bracket assembly
US10138925B2 (en) FRP drive shaft
US20160123378A1 (en) Torque Transmission Mechanism and Vehicle with a Drive Shaft
US20160281767A1 (en) Vehicle propeller shaft
JP4110125B2 (en) Propeller shaft and rotational power transmission mechanism including the same
KR101503113B1 (en) Intermediate Shaft of Steering Apparatus for Vehicle
US11940007B2 (en) Tubular body used for power transmission shaft and power transmission shaft
CN107110228B (en) Torque transmission device
WO2011036890A1 (en) Torque rod
US10941815B2 (en) Connection device for a drive train
JP4945253B2 (en) Shock absorption propeller shaft device for automobile
US20070123359A1 (en) Shock absorbing structure of propeller shaft
CN110953256B (en) Telescopic shaft with stopper
JP2018016128A (en) Telescopic shaft
EP2351655A1 (en) Rolling bearing device for wheel
US20180231050A1 (en) Vehicular propeller shaft
US20110079102A1 (en) Steering apparatus
US20200361240A1 (en) Articulated shaft
JP2018030389A (en) Bearing structure
JP7324589B2 (en) Pipe body and power transmission shaft used for power transmission shaft
WO2016113996A1 (en) Shock absorber
KR101255877B1 (en) Intermediate Shaft of Steering Apparatus for Vehicle
JP7003836B2 (en) Cushioning joint and steering device

Legal Events

Date Code Title Description
AS Assignment

Owner name: BAYERISCHE MOTOREN WERKE AKTIENGESELLSCHAFT, GERMA

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:STREINZ, WOLFGANG;ZEILNER, ARMIN;REINDL, JOHANN;AND OTHERS;SIGNING DATES FROM 20150619 TO 20150715;REEL/FRAME:036545/0799

STCF Information on status: patent grant

Free format text: PATENTED CASE

MAFP Maintenance fee payment

Free format text: PAYMENT OF MAINTENANCE FEE, 4TH YEAR, LARGE ENTITY (ORIGINAL EVENT CODE: M1551); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

Year of fee payment: 4